Rotary pump or engine



Ap 1940- w. EZARYNECKI 2.1953812 aoww rm on ENGINE Filld larch 22. 1938 2 Sheets-Sheet 1 INVENT OR. ZU/MTEz Cum/5cm.

A'T-TORNEY.

April 1940' w/czmnacm 2,195,812

ROTARY PUMP on ENGINE Filed uun 22. 193B 2 Sheets-Sheet 2 Patented Apr. 2, 1940 UNITED, STATES PATENT CFFIGE ROTARY PUMP R ENGINE and Casimer Czarnecki Application March 22, 1938, Serial No. 197,318

6 Claims.

This invention has to do with pumps of the 10 ing application of Walter Czarnecki, Serial No.

168,336, filed October 11, 1937, and entitled Rotary pump.

A rotary pump of the character with which this invention is concerned ordinarily includes a pump housing formed with a cylindrical bore.

A cylindrical rotor is eccentrically mounted within the bore, and this rotor is formed with slots opening into the peripheral surface thereof. It is evident that a crescent shaped space is defined between the periphery of the rotor and the cylindrical bore, and the housing is formed with inlet and outlet openings properly disposed with respect to this crescent shaped space.

Varies are disposed in the slots for sliding action therein, and in order that the proper pumping effects be obtained'it is essential that the vanes be maintained in a position effectively spanning the space between the periphery of the rotor and the bore of the housing.

Prior to the advent of the present invention it has been the practice, in many instances, to avail of centrifugal force which is created as an incident to rotation of the rotor, as well as various other mechanical devices, for the purpose of maintaining the vanes in their effective spanning position.

However, for widely varying reasons the known means employed for this purpose have not .proven to be entirely satisfactory, and this invention has 0 in view, as its foremost objective, the provision of a. rotary pump of the character above noted including novel and improved means for maintaining the vanes in position eflectively spanning the space between the periphery of the rotor'and th bore in the housing.

More in detail this invention has in view, as an important object, the provision of means disposed coaxially with the bore and which rotate with the rotor, and which means causes the vanes to maintain their effective spanning position.

In carrying out this objective in a practical embodiment the invention has in mind the pro-.

vision of a ring element which is designed to present surfaces for engaging the underside of the vanes to maintain the latter in their eflfective (Cl. 103-136) V spanning positions. In actual practice two of these'ring elements .will'be employed, one at each end of the rotor.

A further particular object of the invention is the provision of a ring element of the character 55 above described which is formed with notches opening into the periphery thereof, and which notches are of proper dimensions to accommodate lateral movement of the vanes with respect thereto, and which lateral movement is an in- 10 evitable incident to rotation of the rotor, which takes place on an axis eccentric to the axis of the bore inthe housing and the ring element.

Inasmuch as under many conditions of usage the outer edges of the vanes will contact or engage the bore in the housing it becomes important to reduce to a minimum any friction which may take place between these relatively moving parts.

Accordingly, the invention has in view, as a further objective, the provision, in a rotary pump 20 of the character above noted, of a vane element including a main body portion formed with a groove on its outer edge for receiving a roller, and which roller is intended to engage and roll over the bore in the housing. 5

In view of the-lateral movement between the vanes and the supporting rings formed with the notches which receive the extremities of the vanes, it also becomes important to provide means for reducing friction between these relatively o movable parts, and the invention, therefore, has a further object in view in the provision of a vane including a main body portion the lower edge of which is formed with a cylindrical recess for receiving a roller that engages the bottom 35 edges of the notches in the end rings.

Various other more detailed features and advantages of the invention will in part become apparent, and in part be hereinafter stated, as the description of the invention proceeds.

The invention, therefore, comprises a mechanism intended to function either as a rotary pump or engine and which mechanism includes a housing formed with a cylindricalbore, a cylindrical rotor eccentrically mounted in the bore for rota- 5 tion therein, said rotor being formed with slots opening into the periphery thereof, vanes disposed in said slots and movable therein to effectively span the space between the periphery of the rotor and the bore in the housing, and ro- 50 tating means mounted coaxially with the bore in the housing for maintaining the vanes in their effective spanning position. This rotating means takes the form of supporting rings, one being mounted at each end of the rotor, and which rings I carried by the rotor.

provide a surface for maintaining the extremities of each vane in effective spanning position. This maintaining or supporting surface may be limited in circumferential extent to an amount no more than is necessary to accommodate relative lateral movement between the vanes and the supporting rings, which is an inevitable incident to rotation of the-rotor on an axis eccentric to the axis of the rings.

Another important part of the invention is the particular construction of the vanes which are These vanes preferably consist of a main body portion formed with a cylindrical recess at its outer and inner edges. Anti-friction rollers are disposed in these recesses and are designed to engage the bore of the hous-v ing on one side and the bottom edges of the notches in the end rings at the other.

For a full and more complete understanding of the invention reference may be had to the following description and accompanying drawings, wherein Figure l is a sectional view through the main body por ion of a fuel supply unit constituting the housing for a rotary pump embodying the precepts of this invention,

Figure 2 is 'an enlarged sectional view through the housing and rotor, this view being taken about on the plane represented by the line 22 of Figure 1,

Figure 3 is a view in end elevation developing one of the end supporting rings,

Figure4 is an enlarged detailed view in perspective of one of the vanes in modified from including the rollers,

Figure 5 is an end showing, with parts broken away, developing the relationship of the vanes shown in Figure 4 to the rotor and end rings,

Figure 6 is a view taken on substantially the same plane as Figure 3, but is somewhat enlarged and develops a modified form,

Figure 7 is another view similar to Figures 3 and 6 of still another modified embodiment of the invention, and

Figure 8 is a view taken at right angles to the showing of Figure 7, this view being taken about on the plane represented by the line 8-8 of Figure 7.

Referring now to ,the drawings, wherein like reference characters denote corresponding parts, the housing for the mechanism therein depicted, which in this instance is intended to function as the rotary pump of a fuel supply unit, isidentifled by the reference character B, and which housing may constitute the main body part of a fuel supply unit such as shown in the co-pending applications of Walter Czarnecki above identified.

At this point it is well to note that the housing may take any form consistent with the use to which the mechanism is to be put. For instance, if the mechanism is to be employed as a compressor the housing may be provided with an appropriate water jacket which will perform its obvious cooling functions.

Referring now more particularly to Figure 1, it is noted that this housing B may be made from any appropriate metal which is machined to accommodate the various mechanisms which are carried thereby, and other mechanical organizations which it may be found convenient to attach thereto.

The main body member or housing B is formed with a circularly shaped portion ID that is reduced in diameter as indicated at H, and this portion II is further reduced in diameter and threaded, as represented at l3. Extending throughout the pump housing as defined by the portion In is a bore [4 which terminates in a shoulder represented at 15. From the shoulder 15 through the reduced portion II to the end of the main body part B is another opening or bore designated [6 which is of cylindrical shape having an axis out of alignment with the axis of the cylindrical bore l4. Thus the bore I6 is eccentric to the bore [4.

The wall of the pump housing as defined by the portion I0 is provided with an opening I! which is intended to constitute the inlet for the pump, and which bore may communicate with any source of supply of fluid which is to be affected by the pump.

A second passageway designated 18 is intended to constitute the outlet for the pump, and this passageway may be connected to any desired mechanism which is employed in conjunction with the pump, such as the pressure regulating valve shown in the first mentioned above identified copending application. The flange at l9 may be employed to connect such a pressure regulating valve to the main body part B.

It is notable that the extremities of the passageways I1 and I8 which open into the bore l4 may vary in accordance with any particular requirements. However, as clearly shown in Figure 2, the inner ends of these passageways are preferably enlarged to extend around an appreciable portion of the bore H.

An end closure for the bore I4 is shown at 20, and this end closure is formed with an extension 2| which extends into and snugly fits within the bore I4. This end closure 20 may be secured in position on the main body part B by headed screw bolts 22 which extend through openings in the end closure 20 and are screwed into sockets 23 in the housing It.

The end closure 20 is provided with a' cylindrical socket 24 which is eccentric to the axis of the bore I4, that is the axis of the socket 24 constitutes a continuation of the axis of the bore 16. Thus the axes of the socket 24 and bore I6 are in alignment.

A bushing designated 25 has an outer cylindrical surface which is snugly received in the bore I4. This bushing 25 is provided with a cylindrical bore 26, the axis of which is in alignment with the axis common to the socket 24 and bore I6.

I A shaft referred to in its entirety by the reference character S is shown as having one end received in the socket 24, whereby the latter is constituted a bearing for the shaft. This shaft has an enlarged portion at 27 which is received in the bore 26 so that the bushing ,25 constitutes a bearing for the shaft S.

The enlargement 21 on the shaft provides a shoulder at 28 which lies within an overhanging shoulder 9 formed on the sleeve bushing 25. Received within the shoulder 9 is a sealing ring 29 which engages the face 28 of the enlargement 21. The respective surfaces of the sealing ring 29 and 28 are ground down to provide a required ground fit which creates a seal at this point in a manner to be hereinafter pointed out.

An end bushing 30 is fitted in the end of the bore l6, and this bushing 30 is provided with an end flange 3| which engages the end of the threaded portion l3. A retaining member in the form of a cup 32 has an inner cylindrical wall which is threaded, as shown at 33, and which meshes with the threads l3. This cup member 32 has a bottom 34 which is formed with an opening 35 the axis of which is in substantial alignment with the axis of the bore IS.

A bearing member 36 is received in a socket 3'? which is formed on the bushing 30, and this bearing member 36 has a central bore 98 through which passes the shaft S. It is notable that the inner end of the bushing 30 is of a truncatedconical formation providing a ground surface 39 that is spaced from the shaft S by a recess 40 which may include packing members shown at 4| that encircle the shaft S.

A sealing ring 42 is provided with a ground surface that engages the ground surface 36 to provide a seal, and this ring 42 is formed with an undercut circular recess designated 43. A packing sleeve 44, which preferably is made from an appropriate composition resistant to the effects of oil, such as a rubber composition now available to the public, is snugly disposed about the shaft S, and this packing sleeve 44 preferably has an outer corrugated surface which terminates in an end flange 45 that is received in the undercut recess 43. A retaining ring 46 is fitted about the outer surface of the sleeve 44, and is formed with an extension 41 that engages the flange 45. Extending oppositely from the extension 41 for a distance just a little less than half the length of the packing sleeve 44 is a sleeve 8.

The retaining ring 46 is also formed with a radially extending flange 48 against which abuts a coil spring 49 that is disposed about the sleeve 8.

At the end of the bushing opposite from the sealing ring 29 the enlarged portion 21 projects a slight distance to define a shoulder 56, and abutting the shoulder 50 is a ring 5| that is formed with an undercut recess 52 corresponding to the recess 43 in the ring 42. The packing sleeve 44 has another flange 53 which is received in the recess 52, and maintained therein by another retaining ring 54 which is a substantial duplicate of the retaining ring 46.

The portion ll of the main body part B is formed with an opening 55 which extends into the bore |6, and which opening is ordinarily closed by a threaded plug 56. Obviously lubricant may be introduced into the bore 6 through the opening 55, and after being introduced the opening may be closed by the plug 56.

The outer cylindrical wall of the sleeve bushing 25 is'formed with a groove 51 which communicates with the space defined by the bore l6.

' This groove 51 also communicates with a circular recess 58that extends about the sleeve bushing 25, and a passageway 69 establishes communication between the recess 58and the bore 26. Thus lubricant is supplied to the outer surface of the enlargement 21 and the bore 26 of the sleeve bushing 25;

Referring now more particularly to the showing of Figures 2 and 3, the portion of the bore |4 between the sealing ring 29 and extension 2| of the end closure 26 is designed to constitute a pumping chamber by receiving a rotor 66 which is keyed to the shaft S, as indicated at I. This rotor .60 is of cylindrical formation, and being carried by the shaft S is obviously eccentrically disposed with respect to the bore |4.

Thus the outer periphery of the rotor 60 and the bore |4 define a crescent shaped space. The rotor 60 is formed with a plurality .of slots 6i opening into the periphery of the rotor, and these slots 6| are preferably radially disposed, that is the side walls of theslots 6| are substantially parallel to a radius extending equidistantly therebetween.

Disposed in each of the slots 6| in a relationship, while though snug, permits of sliding movement, are a plurality of vanes 62. In the form of the invention shown in'Figures 2 and 3 the vanes 62 are of 'a simplified construction having outer edges at 63 which are curved corresponding to the curvature of the bore M with which they engage. These vanes 62 are intended to effectively span the space between the outer periphery of the rotor 60 and the bore i 4, to provide the required pumping effects as an incident to rotation 0f,the rotor 60. Obviously as the rotor turns it is necessary that the vanes 62 move in the slots 6|, to maintain their required effective spanning positions.

Disposed between the rotor 60 at one end and the extension 2| of the end closure 20 is an end supporting ring designated 64, and another duplicate' ring is positioned between the other end,

of the rotor and the sealing ring 29.

Each of the rings 64 has a-diametrical dimension substantially the same as the bore l4, and these rings are coaxial with the bore I4. Deflning a ring structure is a central opening 65 having a radius which exceeds the radius of the shaft S within the bore M by the distance between the axis ofthe shaft S and the bore l4, plus any required mechanical clearance. This dimension of the opening 65 is required so that the end rings 64 may rotate with the rotor in the bore l4, in a manner to be hereinafter pointed out.

Each of the rings 64 is formed with a plurality of notches 66 which open into the periphery of the rings, and these notches are intended to correspond in number and relative position to the slots 6| in the rotor. The vanes 62 project beyond the rotor 66 at each end into the notches 66, with the bottom surfaces of the notches 66 designated 61 engaging the underside of the vanes to maintain them in effective spanning position. Each of the notches 66 must have a width sufliciently great to accommodate relative lateral movement of the vanes 62 in the notches, and which lateral movement is an inevitable incident to rotation of the end rings 64 with the rotor 60.

Speaking with reference to the showing of Figure 3, when one of the vanes 62 is in either of the vertical positions a radius passing through the center of the -vanes will, of'course, pass through theaxis of the rotor, and in this vertical position will pass through the axis of the end ring 64. However, as the rotor and end ring rotate together, the radii passing through the centers of the vanes and notches 66 respectively gradually come out of alignment, thus causing the vanes to move relative to the notches in the end ring.

I When rotation has proceeded through 90 a vane in a vertical position will have moved, with respect to an end ring, a distance equal to the distance between the axes of the rotor and end ring. When rotation has been continued through another 90 the vane will have returned to its original position with respect to the end ring. However, when rotation is continued through still another 90 the vane will have moved in a direction opposite to that from the movement first above referred to, and to the extent of the distance between the axes of the rotor and ring During the final 90 of rotation the vane will have; returned to its original position with respect to the end ring.

Thus it is evident that each notch in the en ring must be sufliciently wide to allow for a movement of the vane with respect thereto in opposite directions, and to an extent in each direction equal to the distance between the axes of the rotor and ring. Therefore, each notch must have a width equal to the thickness of the vanes plus twice the distance between the axis of the rotor and ring, and in addition any space required for mechanical clearance.

It is believed that certain beneficial results attach to having these notches accurately dimensioned so as not to provide any unnecessary excess in their width, although if the notches are at least as wide as the thickness of the vanes, plus twice the distance between the axis of the rotor and ring, they may exceed this minimum to any extent and still leave an operable mechamsm.

It is important to note that the bottom surfaces 6'! of each of the notches 66 are of a curvature defined by an are drawn on the same center as the outer periphery of the rings 64.

It is evident that the outer edges 63 of the vanes 62 are at all times maintained in engagement with the bore I4, due to the supporting effects of the surfaces 61 of the notches 66 in the end rings 64. Therefore, as the rotor 60 is rotated by the shaft S there is a relative sliding motion between the vanes 62 and the walls of the slots 6|.

Thus, if the rotor 60 is rotated in a counterclockwise direction, speaking with reference to the showing of Figure 2, fluid will be drawn in from the inlet l1, and due to the crescent shape of the space between the periphery of the rotor 60 and the bore [4 attenuation will be provided to suck or draw the fluid in.

However, as this crescent shaped space decreases towards the outlet opening l8, the effect of the vanes thereon will be to build up pressure in the fluid and force the same through the outlet opening l8 under increased pressure.

In the form of the invention illustrated in Figures 1, 2 and 3, the vanes 62 are shown as of a simplified construction. However, due to the fact that the outer edge 63 of each vane, under the usual conditions of operation, will frictionally engage the bore l4, it is important to reduce this friction to a minimum, and it has also been found desirable to reduce any friction between the bottom edges of the vanes 62 and the edges 61 of the notches 66. Accordingly, Figures 4 and 5 develop a somewhat different type of arrangement involving particularly a vane of novel construction.

In this form the vane is referred to in its entirety by the reference character V, and is shown as consisting of a main body portion 68 that conforms generally to the shape of the vane 62 in that the side walls of the main body portion 68 are intended to snugly engage the side walls of the slots 6| in the rotor 60. However, the outer edges of the body portion 68 are formed with a cylindrically shaped recess 69 that preferably has an extent something greater than half a cylinder, as shown in Figure 4.

A roller 10 is positioned in the recess 69 and maintained therein by the overhanging shoulders formed in the main body portion 68 and defined by the recess 69, which exceeds half a cylinder. The roller 10 will preferably have a diameter corresponding to the distance between the axes of the rotor and the bore I4. It is evident that this roller 10 is designed to roll along the bore M as the vane V spans the distance between the periphery of the rotor 60 and the bore M.

The bottom edge of the main body portion 68 of the vane V may also be formed with a cylindrical recess II that corresponds to the recess 69 in the top edge, and which recess 1 I also preferably exceeds half a cylinder.

A second roller 12 is positioned in the recess in a manner similar to the positioning of the roller 10, and this roller 12 is intended to engage the bottom edges of the notches which are formed in the end rings.

As shown in Figure 5, when the vanes V are used a slightly different shape of notch in the end rings 64 is employed, such a notch being designated 13. The notch 13 is formed with the usual side walls 14, and a bottom wall 15 that has a curvature of a circle taken with the axis of the ring as the center. However, the bottom wall I5 merges in with the side wall 14 at each side by the curved portions 16. Thus it is evident that the vanes V may move laterally in the notches 13, with the roler l2 rolling along the bottom edges 15 to reduce friction at these points.

Another form of the invention is depicted in Figure 6, and in this form the vanes are shown as carried by the rotor in an inclined or angular position as compared to the radial disposition of the vanes developed in Figures 1, 2 and 3. It will be noted that the rotor 60 is formed with slots that are defined by spaced parallel walls, and a plane passing equidistantly between these spaced parallel walls and in parallel relationship thereto will not be a radius of the rotor. Received in each of the slots 80 is a vane, and in the form of the invention shown in Figure 6 the vanes may be one of the vanes V illustrated in Figure 4.

The end ring 64 of the form shown in Figures 1, 2 and 3 is replaced by an end ring 8| formed with notches 82 corresponding in position and angular disposition to the slots 80 in the rotor. In order to accommodate the movement of the vanes V, which project at each end into the end rings 8|, in the notches 82, the latter must have a lateral dimension equal to twice the distance between the centers of the ring and rotor respectively, plus the thickness of the vanes and any mechanical clearance required, following the rule above worked out.

It will be noted that the bottom wall of each of the notches 82, which is designated 83, will have a curvature defined by a radius equal to the radius of the end ring and swung about a center that is offset with respect to the center of the end ring. A different center is used in defining each surface 83, and will be offset to a degree corresponding to the angular disposition of the vanes. Thus the surface 83 might be said to be parallel to the bore M.

It is important to note that in computing the lateral dimension of the notches 82 their width will be taken in a direction normal to a radius passing through the center of the notch, this direction being in an acute obtuse-angular relationship with respect to the side walls 82, rather than in any right-angular relationship.

With the vane V inclined in the manner shown in Figure 6 the rotor may be rotated in either direction. If the vane V is replaced by one of the simple vanes 62 the angular arrangement shown in Figure 6, together with a rotation of the rotor in a clockwise direction (speaking with reference to thesame showing) will provide a good wiping action with the bore l4. On the other hand, if any of the vane constructions is employed, rotation in a counter-clockwise direction together with the angular disposition of the vane will evidence good compressive effects on the fluid.

Still another form of the invention is shown in Figures '1 and 8. in this form the end rings 6t are replaced by end supporting rings 85. Each of the end rings as has a radius which is equal to the radius of the cylindrical bore l4, and these end rings 355 are formed with notches correspond ing to the notches 66 which are designated 88. These notches 89 have a depth corresponding to the width of the vanes 82, and the width of the notches is worked out in accordance with the above announced rule, that is they are equal to twice the distance between the axis of the rotor and ring respectively, plus the thickness of the vanes.

As clearly shown in Figure 8, the vanes 62 are carried by the rotor 88 in the slot Bl in the manner above described in connection with Figures 1, 2 and 3, and which extremities project into the notches 89 of the end rings 85 with the bottom surfaces of these notches 89 constituting means for maintaining the vanes in effective spanning position.

Each of the rings 85 is intended to rotate with the rotor, and in many cases it has been found desirable to provide means independent of the vanes for driving the end rings 85 from the rotor. To this end each of the end rings is formed with a plurality of openings 86 which preferably are circular.

Received in each of the openings 86 is 9. lug 81 that projects from the end wall of the rotor 68. These lugs 81 are shown as separate pieces that are carried by the rotor by being snugly received in the recesses formed therein. By availing of a pressed fit all likelihood of the lugs accidentally falling out is obviated. It is evident that the end ring 85 rotates on an axis that is the axis of the cylindrical bore l4. Hence rotation of the rotor 58 is eccentric with that of the rings.

it ,Thus, relative movement between the several lugs 81, which are fixed parts of the rotor and the rings, must be accommodated. The movement of the lugs with respect to the end ring will not only be lateral or circumferential, but will also be radial. Thus the circular openings 88 readily accommodate both components of this movement, and inaccordance with the rule above announced the diameter of each of the openings 85 must be equal to twice the distance between the centers of the rotor and bore M, respectively, plus the thickness of the lug 81 and any required mechanical clearance.

It is also notable that the ring 85 has a central opening 88 which encompasses the shaft 8, and due to the eccentricity between the rotor and shaft this opening must be sufficiently large to allow for rotation of the ring. This is provided for by having the radius of the opening 88 exceed the radius of the shaft S by an amount at least equal to the distance between the centers of the shaft and ring.

While Figures 7 and 8 develop four of the lugs 81 in the respective openings 88 in the end rings in which they are received, this number may be varied as occasion demands. It is particularly important to note that while any required number of lugs may be employed to cause the end ring 85 to rotate, the number of vanes 62 is in no way dependent on the particular number of openings 86. Thus eight vanes may be employed in conjunction with only four of the lugs 81, or any other number of vanes found desirable.

While preferred specific embodiments of the invention are hereinbefore set forth it is to be clearly understood that I am not to be limited to l the exact constructions illustrated and described, because various modifications of these details may be provided in putting the invention into practice within the purview of the appended claims. I

I claim:

1. A rotary pump of the character described comprising a main body part formed with a circular bore to define a pump housing, a rotor element eccentrically mounted for rotation in said housing, said rotor element being formed with a plurality of radially disposed slots having parallel side walls, a vane having parallel faces in each of said slots and having its faces in slidable engagement with the side walls of said slot, each .of said vanes having an edge in engagement with the bore defining the housing and which engagement is maintained during a complete revolution of the rotor with respect to the housing, and a pair of end rings associated with the rotor element, there being a ring at each end of the rotor, said end rings being mounted coaxially with the bore defining the housing and having the same diametrical dimension as said bore, each of said rings being formed with a plurality of notches opening into the periphery thereof and having arcuate bottom surfaces and which notches correspond to the slots in the rotor, each of said notches having a width equal to twice the distance between the axes of said rotor and rings, plus the thickness of a vane, said vanes projecting beyond the rotor element at each end and into the notches in the i distance between the periphery of the rotor and the cylindrical bore to cause a building up of pressure on fluid in said space between the rotor and bore as an incident to rotation of the-rotor, and a pair of end rings associated with said rotor and disposed in said bore, there being a ring at each end of the rotor, said rings being coaxial with the cylindrical bore and having peripheral notches of a width equal to twice the distance between the axes of the rotor and bore plus the thickness of the said vane means and a depth equal to the height .of said vane means plus mechanical clearance, said notches having arcuate bottom surfaces and said vane means projecting beyond the rotor element at each end and into the notches in said rings, whereby the bottom edges of said notches are in supporting and sealing contact with said vane means.

3. A rotary pump of the character described comprising a pump housing formed with a cylindrical bore, a shaft mounted in the pump housing on an axis eccentric to the axis of-the cylindrical bore, a rotor drivably carried by said shaft within said pump housing, said rotor being formed with .slots opening into the periphery thereof, vane asedges, a roller snugly received in each of said grooves, one roller of each assembly being in rolling and sealing engagement with the wall of said bore, and a pair of end rings associated with the rotor and disposed in said cylindrical bore, there being a ring at each end of the rotor, said rings being coaxial with the cylindrical bore, and formed with central circular openings, said central openings having a radius which at least exceeds the radius of the said shaft by the distance between the axis of the shaft and the axis of the cylindrical bore, the said shaft passing through said openings, said end rings being formed with peripheral notches of a width substantially equal to twice the distance between the axes of the shaft and cylindrical bore plus the thickness of one of the vanes, said peripheral notches receiving extremities of said vane assemblies for holding the latter in said spanning relationship during rotation of the shaft, rotor, vanes and rings with one roller of each vane assembly in rolling and sealing engagement with the bottom wall of its respective peripheral notch.

4. A rotary pump of the character described comprising a housing formed with a cylindrical bore, a rotor mounted for eccentric rotation in said bore, said rotor being formed with a plurality of slots opening into the periphery thereof, vanes carried by said slots, there being a vane in each of the slots, said vanes effectively spanning the distance between the periphery of the rotor and the cylindrical bore to cause a building up of pressure on fluid in said space between the rotor and bore as an incident to rotation of said rotor, and a ring rotatably mounted concentrically in said bore at the end of said rotor and formed with a plurality of peripheral notches of a width equal to twice the distance between the axes of said rotor and rings, plus the thickness of one of said vanes and corresponding in number and relative position to the slots in the rotor so as to cause each side wall of said notches to come into alignment with the corresponding wall of a rotor slot once during a complete revolution of said rotor and ring, each of said notches in the ring having a bottom surface of a curvature defined by a radius swung on the center of the ring, said notches receiving said vanes with the bottom edges of the vanes in sealing engagement with the bottom surfaces of the notches whereby the vanes are held in spanning relationship during the rotation of the rotor, vanes and rings.

5. A rotary pump of the character described comprising a housing formed with a cylindrical bore, a rotor mounted for eccentric rotation in said bore, said rotor being formed with a plurality of slots opening into the periphery thereof, vanes carried by said slots, there being a vane in each of the slots, said vanes effectively spanning the distance between the periphery of the rotor and the cylindrical bore to; cause a building up of pressure on fluid in said space between the rotor and bore as an incident to rotation of said rotor, and a ring formed with a plurality of notches in the periphery thereof, each of said notches having side walls and a bottom wall, the side walls being spaced apart a distance equal to twice the distance between the axes of the bore and rotor plus the thickness of a vane, the bottom surface having a curvature defined by a radius swung on the center of the said ring, said vanes having portions extending into said notches with the bottom edges of the vanes resting on the bottom surfaces of the notches whereby the vanes are held in spanning and sealing relationship during rotation of the rotor, vanes and rings.

6. A rotary pump of the character described comprising a housing formed with a cylindrical bore, a rotor mounted for eccentric rotation in said bore, said rotor being formed with a plurality of slots opening into the periphery thereof, vanes carried by said slots, there being a vane in each of the slots, said vanes effectively spanning the distance between the periphery of the rotor and the cylindrical bore to cause a building up of pressure on fluid in said space between the rotor and bore as an incident to rotation of said rotor, and a ring formed with a plurality of notches in the periphery thereof, each of said notches having side walls and a bottom wall, the side walls being spaced apart a distance equal to twice the distance between the axes of the bore and rotor plus the thickness of a vane, the bottom surface having a curvature defined by a radius swung on the center of the said ring, said vanes having outer edges of a curvature corresponding to the curvature of the bore and inner edges corresponding to the curvature of the bottom walls of said notches, the bottom edges of the vanes being supportingly and sealingly engaged by the bottom surfaces of the notches whereby the vanes are held in spanning sealing relationship during rotation of the rotor, vanes and rings.

WALTER CZARNECKI. 

